Positive synchronizing coupling mechanism for power transmission



H. slNcLAlR ET AL 2,320,757 POSITIVE SYNCHRONIZING COUPLING MECHANISM FOR POWER TRANSMISSION Filed July s1, 1940 8 Sheets-Sheet l 22M/...LW

l A. .El

June l, 1943.

June 1, 1943. H, slNcLAlR ET Al.

POSITIVE SYNCHRONIZING COUPLING MECHANISM FOR POWER TRANSMISSION Filed July El, 1940 8 Sheets-Sheet 2 June 1, 1943.

H. SINCLAIR ET AL POSITIVE SYNCHRONIZING COUPLING MECHANISM FOR POWER TRANSMISSION Filed July 3l, 1940 8 Sheets-Sheet 3 @Izzy fz June l, 1943. H. slNcLAlR ET Al.' 2,320,757

POSITIVE SYNCHRONIZING COUPLING MECHANISM FOR POWER TRANSMISSION Filed July 51, 1940 f 8 Sheets-Sheet 4 8 Sheets-Sheet 5 H. SINCLAIR ETAL POSITIVE SYNCHRONIZING COUPLING MECHANISM FOR POWER TRANSMISSION Filed July 31, 1940 June 1, 1943.

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June 1, 1.943. H. slNcLAlR ET AL. 2,320,757

POSITIVE SYNCHRONIZING COUPLING MECHANISM FOR POWER TRANSMISSION Filed July s1, 1940 8 Sheets-Sheet 7 June 1, 1943. H. slNcLAIR ET Al. 2,320,757

POSITIVE SYNCHRONIZING COUPLING MECHANISM FOR POWER TRANSMISSION Filed July 51, 1940 8 Sheecs-Sheel 8 lPatented June l, 1943' POSITIVE SYNCHRONIZING COUPLING MECHANISM FOB POWER TRANSMIS- SION Harold Sinclair, London, and Robert Cecil Clerk,

Egham, England, assigner-s to Hydraulic Couplings Patents Limited, London, England, a company oi Great Britain Application July 31, 1940, Serial No. 348,706 In Great Britain August 19, 1939 This invention relates to coupling mechanism of the self-shifting kind. namely of the kind capabie of engagement in response to torque acting in one sense through the mechanism and of disengagement in response to the application of torque in the'opposite sense.A

'I'he invention is concerned with positive synchronizing coupling mechanisms of this kind including a. first member, which may be for example the driving member or the driven member of the mechanism, a second member which may be the driven member' or the driving member of the mechanism, and which is rotatable relatively to the first member, an intermediate member in driving connection with the second 1 member and capable of sliding relatively to the first and second members into and out of meshing engagement with the rst member, and a.

subsidiary ratchet drive between the rst and intermediate members operative while these members are disengaged to synchronize them for meshing cleanly (i. e. with exact registering of the intermeshing teeth) together when the rst and second members are urged to rotate relativedrive preferably being rendered inoperative by complete engagement of the first and intermediate members.

In such mechanism at present in use, examples or which are described in the Specification of United Kingdom Patent No. 486,589, the second member is a. shaft provided with helical splines and the intermediate member is a sleeve having corresponding internal helical splines co-operating with the splines on the shaft. When torque acts between the sleeve and the shaft, the splines co-operate to shift the sleeve along the shaft and thereby cause clutch teeth on the exterior of the sleeve to engage with or disengage from clutch teeth on the rst member.

The internal helical splines in the sleeve are machined by a broaching operation, and while this is convenient for mass productionof large quantities, the machining cost is unduly high in 45 the production of relatively small batches.

Accordingly one object of this invention is to provide an alternative form, of such positive synchronizing coupling mechanism which can be more cheaply machined in small batches.

When the synchronizing coupling mechanism is used as a gear-seelcting clutch in change-speed or reversing gearing, the known kind of intermediate member referred to also occupies a substantial length of shaft, and a further object ofv (ci. 'i4-337) this invention is to provide an alternative oonstruction of reduced axial dimensions.

Another object is to provide in such positiv synchronizing coupling mechanism improved"` means operable for rendering the mechanism bidirectionally free and improved means operable for locking the mechanism in a condition in which it is adapted to transmit toi-ques in both senses.

10 A further object is to provide in positivesyn-- chronizing coupling mechanism of the kind here-4 inbeiore referred to, a second member in the form of a slidable helical toothed gear wheel. In this form the improved mechanism is particularlyi adapted for use as gear-selecting mechanism-.

in change-speed and reversing gearing, sinceth'eUV helical gear wheels may be constituted by 1 ofthe gearing that would be essential, irrespec n tive of the kind of gear-selecting clutch mechr anism employed, and the length of the gearing is accordingly relatively short. With this form of the improved arrangement, under certain circumstances frictional effects may prevent v l .n ly to each other in one sense, the auxiliary ratchet 2U the deslred s idmg of the l termedia'te member unless suitable precautions are taken, and it is another object to provide such a construction in which frictional eiects do not interfere with the desired sliding.

30 Another object is to provide positive syn- 35 Further objects and advantages of the invention will be apparent from the following' description of examples thereof shown in the accompanying drawings, in which Fig. 1 isa sectional side elevation of a marine versing' gearing, taken on the line l-I in Fig. 2,

Fig. 2 is a sectional end elevation on the line 2-2 in Fig. 1.

Fig. 3 is a. sectional view of a detail of this gearing taken on the line 3 3 in Fig. 1,

Fig. 4 is a developed view a detail taken. on the line 4 4 in Fig. 3,

Fig. 5 is a diagram of control mechanism,

50 Fig. 6 is a diagram of a marine propelling 5s Fig. 13 is a. diagrammatic section of a twospeed synchronizing self-shifting gear arranged to give a bidirectional drive on each speed,

Fig. 14 is a sectional elevation of the control mechanism of the gear shown in Fig. 13 taken o'n a plane parallel to and behind that of Fig. 13.

Fig. 15 is a sectional plan on the line I5-I5 in Fig. 14,

Fig. 16 is a sectional elevation, taken on the line Ilia-1 6 in Fig. 20. of a four-speed gear suitable for locomotives,

Fig. 17 is a section of a detail of the gear shown in Fig. 16.

Fig. 18 is a developed view of parts of the gear shown in Fig. 16,

Fig. 19 is a side elevation of part of a powertransmission system embodying the gear shown in Fig. 16, showing control mechanism partly in section,

Fig. 20 is a diagrammatic end elevation of the gear as viewed from the left of Fig. 16, and

Fig. 21 is a diagrammatic sectional side elevation of an alternative form of improved synchronizing self-shifting coupling.

The gearing shown in Figs. 1 to 12 comprises an input shaft i coupled to the marine engine 35 by a hydraulic coupling 35 of the kinetic type (Fig. 6). The shaft I0 is provided with a ange II (Figs. 3 and 4) on the periphery of which are cut outwardly projecting `iaw-ciutch teeth I2, which are of double-helical type having a helix angle of 15 deg. The front halves of these teeth (that is the halves nearer the engine) follow a right-handed helix. On the shaft I0 in front of the flange II is journalled and slidable a forwardv driving gear wheel I3 having left-handed helical teeth with a helix angle of 30 degrees. Integral with this gear wheel is a rearwardly directed tubular projection I4 having internal right-handed l deg. helical teeth I5 adapted to mesh with the front halves of the jaw-clutch teeth I2. On the front of the flange II are pivoted one or more pawls such as I5 (Figs. 3 and 4) the noses of which point in the, anti-clockwise direction (as viewed from the front) and are bevelledl to cooperate with the jaw-clutch teeth I5 when the wheel I3 is in such a position axially of the shaft I0 that the jaw-clutch teeth I5 are spaced slightly from the teeth I2. The pawls I5 are pivoted on pins IBA fast in the flange I I, and their noses are urged outwards by hair-pin springs IGB located by pins ISC also fast in the flange II. These springs are omitted from Fig. 4.

On the shaft I0 behind the flange II is journalled and slidable a reverse driving gear wheel I1 having right-handed 30-deg. helical teeth and a forwardly-directed tubular projection I3 having internal left-handed -deg. helical teeth I9 adapted to mesh with the rear halves of the jawclutch teeth I2 under the control of one or more pawls such as 23 pivoted on the back of the flange I I and having their noses also pointing inthe anti-clockwise direction (as viewed from the front) and bevelled to co-operatel with the jawclutch teeth I9.

The forward gear wheel I3 is in constant mesh with a.driven gear wheel 2l fast on an output shaft 22 which is directly coupled to or which forms the propeller shaft, and the reverse gear wheel I1 is in constant mesh with an intermediate wheel 23 which may be fast on a lay shaft 24 to which is also fixed a second intermediate wheel 25 in constant mesh with the driven gear wheel 2I.

The control mechanism includes means, such l0 face 3| on the casing 31 of the gearing for retaining, when required. this gear wheel in its rearmost position in which the forward jaw-clutch teeth I5 are engagedwith the teeth I2. This thrust bearing may consist of a ring 21 provided 1.1 with standard type Micheli thrust pads 23 bearing against the front face of the forward gear wheel I3. This ring is provided with a fork 33 which is engaged on arod fixed in the casing, so that the ring I1 is prevented from rotating.

Si) An arcuate wedging and abutment member 23.

the rear face of which may be bevelled al; 33 in the form of a part of a shallow conical frustum, is displaceablc radially of the driving shaft I3 and adapted to be inserted between the thrust .1 ring 21 and the gear casing, preferably in the neighbourhood of the line of engagement of the pair of gears I3, 2l of the forward train. A similar but oppositely directed thrust, wedglng and abutment assembly 21R, 2BR is disposed behind "l the reverse driving wheel I1, the two wedging and abutment members 29 and 29B being movable radially of the driving shaft in opposite senses by a common control lever. The wedglng member 29 is carried by parallel links 32 one of 15 which is xed to' a shaft 33 journalled in the casing 31. 'I'he wedglng member `29H. is carried by parallel links 32B, one of which is fixed to a shaft 33R journalled in the casing. The shafts 33 and 33B. are constrained .to rotate in unison by a matically in Fig. 5 and. includes a lever 40 i'lxed link 34 and arms 33 and 3BR.

The control mechanism is shown diagramto the shaft 33 and movable in a fixed quadrant 4I. The lever 40 is provided with a latch pin 42 projecting from a rod 43 which can be displaced against a return spring 45 by a grip lever 44. 'I'he latch pin can engage in three notches in the quadrant 4I, these notches being denoted respectively by Ah (ahead), N (neutral), and As (esterni.

'I'he back-turning brake 26 includes a drum 46 keyed to the shaft I0. A tubular boss 41 is xed to the casing 31 (Fig. 1) and on it is lournailed a rocking bracket 48 on which are pivoted at 49 two brake shoes 50, which are normally contracted by a spring 5I. The shoes can be expanded into contact with the drum 45 by a cam shaft 52 actuated by a lever 53. The bracket 43 is normally retained in the position shown in Fig.

5 by a relatively/,strong spring 54 which retains an arm 55. integral with the bracket 43. against a fixed stop 56.

A contracting link formed by a fluid pressure motor 51 is connected between`the lever 53 and a fixed pivot 53. 'I'he motor 51 is controlled by a valve 59 having a piston 50 connected to the rod 43 of the latch mechanism of the control lever 43. When this lever is latched in any of the three notches in the quadrant 4I, the cylinder of the motor 51 is in communication with an exhaust pipe 5I. When the lever 45 is unlatched. the motor cylinder is in communication with a fluid pressure supply pipe 52.

When the control .lever 4G is in the neutral- 19e-evi position as shown in Fig. 5 and the engine is running, 4thebrake 29 and both jaw clutches are disengaged, and the' driving gear wheels I3 and I1 lare restrained axially by the members 29 and .tions clearly understandable.)

In order to put the gear into the astern condition the latch grip lever 44 is now actuated to raise the latch pin 42 from the notch N. Pressure fluid is consequently admitted to the link 51 which begins to contract, moving the cam-shaft 52 counter-clockwise (as viewed in Fig. 5) and engaging the shoes 59 with the drum 46, which is rotating in the direction shown by the arrow in Fig. 5, so that the shaft I9 is arrested, the hydraulic coupling 36 permitting the engine to continue idling. While the shaft I is being arrested, the spring 54 holds the bracket 48 in the position shown in Fig. 5, with the lever 55 against the stop 55. As soon as the shaft I9 has come to rest, the link 51 is able to contract further, so that the lever 53, the bracket 48, the brake shoes 59, the brake drum 46 and the shaft I9 are caused to rock backwards as a whole; consequently pawls of both sets I6 Aand 29 engage jaw clutch teeth I and I9, and the torque thereby applied to the gear wheels I3 and I1 causes them to slide towards each other, as a result of the reaction of their helical teeth, assisted by the reaction of the pawls on the helical jaw clutch teeth, until both jaw clutches are fully engaged and the gearing consequently resists further backward rotation. The control lever 49 is now moved to the astern position and causes the reverse wedging and abutment member 29R to assume its fully operative position behind the reverse thrust ring 21R (Fig. 8) and the forward wedging and abutment member 29 to assume its completely inoperative position. When the latch pin 42 drops into the notch As, the vcontracting link 51 is de-energized and the springs 5I and 54 restore the brake 29 to the disengaged condition shown in Fig. 5. The shaft I9'then begins to rotate forwards (as indicated by the arrow thereon in Fig. 1) and the engine is accelerated.

Since the reverse driving wheel I1 is prevented by the thrust pads 29Rfrom sliding rearwards on the 'input shaft I9 under 'the reactions of its helical teeth and of the co-operating Jaw-clutch teeth I2 and I9, the reverse jaw clutch I2, I9 remains locked in engagement and the reverse gear train I1, 23, 25, 2| drives the output shaft 22. 'I'he operation of the forward gear train I9, 2| has meanwhile caused the forward driving wheel I3 to slide to the front as a result of the reactions of the helical teeth of the gear wheels and 'or the jaw clutch teeth l2 and l5 untu the forward jaw clutch I2, I'5 has disengaged (Fig. 9), the light friction of this wheel on its bearing being suillcient to cause it to assume its foremost .position sothat the pawls I9 of the forward jaw clutch also are inoperative. Forward drive is engaged from neutral in a similar manner.

When it is desired to change from astern to 4alioil the engine is retarded, and the control `rle'ver 49 is unlatched and immiately moved tojwards the ahead positionuntil the bevelled surface '99 on the wedging and abutment member y129associated'lwiththe previously idle lforward c Ross REFERENCE gear train slides the driving pinion I3 of that train far enough towards the ilange II to bring the jaw-clutch teeth I5 into co-operation with the pawls I G (Fig. Unlatchlng of the lever 42 has caused the back-turning brake 26 to be applied, with the result that the gearing and shafts are arrested and thereafter caused to rock in the opposite direction. Since the brake takes an appreciable time to bring the gearing and shafts to" rest, the member 29 will have displaced the pini-n I9 far enough to bring the teeth I5 I into the path of the pawls I6 before the gearing and shafts are rocked in the opposite direction. Thls'back-turning effect, owing to the reaction of the helical gear-wheel and jaw-clutch teeth, maintains the reverse clutch I2, I9 engaged and causes the forward clutch I2, I5 to be drawn into full engagement, the reaction of the pawl I9 and the tooth I5 with which it is engaged assisting the sliding movement of the parts, whereupon the gearing resists further backward rocking. The forward wedging and abutment member 29 is now free to'engage fully in front of the thrust ring 21, as shown in Fig. 1l, while the reverse wedging and abutment member 29B assumes its inoperative position as the lever 49 is moved to engage the latch pin 42 in the notch Ah. As this lever latches home, the back-turning brake 26 disengages and the engine is accelerated. Since the forward driving wheel I4 is prevented by lthe thrust pads 29 from sliding forward on the input shaft I9 under the reactions of its helical teeth and of the helical clutch teeth I2 and I5, the forwardV jaw clutch I2, I5 remains locked in engagement and the forward gear train I3, 2| drives the output shaft 22. 'Ihe operation of the reverse gear train has meanwhile caused the reverse vdriving wheel I1 to slide to the rear as a result of the reaction of the helical gear-wheel and jaw clutch'teeth until the reverse jaw clutch I2, I9 has disengaged (Fig. 11).

The change from forward to reverse is made in a corresponding manner, the conditions while the parts are being retarded by the brake 25 being shown in Fig. 12.

The gearing shown in Fig. 13 has parallel input and outputl shafts 99 and 9|, and the two axially slidable right-handed 30-deg. helical gear wheels 92 and 93 for giving the alternative ratios are journalled on the input shaft 99 and are in constant mesh respectively with left-handed helical gear wheels -94 and 95 fast on the output shaft. Jaw-clutch teeth 99 on the interior of a tubular extension 91 of the-wheel 99 are adapted to mesh with clutch teeth 98 on a flange 99 on the shaft 99 under the control of pawls |99 pivoted on the flange 99 and ldirected anticlockwise as viewed from the left-hand side. 'Ihe wheel 92 has jawclutch teeth |9I on the interior of a tubular extension |92 adapted to mesh with the teeth -98 under the control of pawls |93 which are directed clockwise. The jaw-clutch teeth 99, 99 and I9I, and the noses of the pawls |99 and |93 are 'arranged on l5-deg. left-handed helixes. The ends of the tubular extensions 91 and |92 are maintained adjacent to. one'another by a flanged shroud |94 which is fixed to the wheel 93 and which serves, with these extensions, as a gauging connection between the wheels 92 Aand 93. The wheels 92 and 93 are provided with vv-thrust rings |95 and |96 arranged similarly tothose .shown in Fig. 1. Control means include two .displaceable abutment members |91 and |99 which are respectively rigid with vertically slidable bars |99 and II9 (Fig. 14) provided with SEARCH Roon4 slots accomodating guide pins ||2 screwed into the gear casing ||3. The bars |05 and |I0 are provided with pins ||4 and I|5 with which are engaged levers IIE and 'I I1. The latter lever is journalled on a control shaft ||0 which in turn is journalled in a boss IIS in the casing ||3 and the lever ||6 is iournalled on the boss of the lever I|1. A plate rigid with the shaft II3 carries pins |2I and |22 engaged respectively in arcuate slots |23 and |24 in the levers ||0 and ||1, and springs |25 and |26 urge these levers upwards so that the pins will lie in the lower ends of the slots. A crank |21 fixed to the shai't |l0 is connected to a control handle not shown.

Low gear is established as follows. It will be assumed that the parts are in the configuration shown in Fig. 13 and are stationary. The control shaft ||8 is rocked clockwise as seen in Fig. 14

so that the spring |25 urges the lever ||6 up wards and causes the abutment member |01 to press upwards against the periphery of the thrust ring |05.

' The shaft 90 is now set in rotation in the direction indicated by the arrow inFig. 14, and a pawl |03 engages a tooth I0| and thus causes the teeth 98 and |0| to mesh together in consequence of the reactions of the helical gear wheel and jaw-clutch teeth. The wheel 92 now abuts against the pivot pins of the pawls |03. Thereupon the spring |25 operates to raise the abutment member |01 into position behind the thrust ring |05. While low gear is engaged the pawls |00 do not click over the teeth 96.

To change to high gear the control shaft IIB is urged in the anti-clockwise direction so that it returns to the position shown in Fig. 14, withdrawing the abutment member |01 to its inoperative position, and thereafter moving further to cause the abutment member |08 to press upwards against the periphery of the thrust ring |06. The driving shaft 90 is now retarded, andthe the teeth 33 and the pawls |00 ratchet over the teeth 53. At first the lpawls |03 will ratchet overv the teeth |0|, btt, as the speed of the shaft tends to exceed that of the wheel 32, a pawl |33 engages a tooth |0| and low gear is established as previously described.

The gear shown in Figs. 16 to 20 yields four speeds in both directions of rotation of the uitimate driven shaft. the changes to higher speeds being eected without complete interruption of torque,.in accordance with .Patent No. 2,011,734.

A primary shaft |30 is connected to an interuel-combustion driving engine A (Fig. 19) by a hydraulic coupling 30A. This shaft rotates in the direction of the arrow shown in Fig. 16 and isjournalled in a gear case |3| by a deep-groove ball bearing |32 and a roller bearing |33. A secondary shaft |34 is iournalled in the gear case by a thrust bearing |35 and three roller bearings |35. A bevel pinion shaft ,|31 is disposed parallel to the shafts |30 and |34 and is integral with a pinion |30 meshing with abevel wheel |35 fixed to a transverse shaft |40 which is connected by reduction gearing, not shown, to the driving axles of the locomotive. Fig. 20 shows clearly the relationship of the several gear shafts.

inertia of the load causes the wheel 92 to overrun the shaft 90. so that this wheel moves to the left in consequence of the reaction of its helical teeth assisted by the reaction of the helical clutch teeth 90 and I|||, the wheel 90 drawing with it the wheel 93 through the agency of the ganging connection |04 until the clutch teeth come into the path of the pawls |00; when the speed of the shaft 90 tends to drop below that of the wheel 93. a lpawl |00 engages a tooth 30 and moves the wheels 93 and 02 to the left, under the inuence of the reaction of the helical teeth of the wheel 53 assisted by the reaction of the pawl |00 on the helical tooth 9S, until the teeth and 98 aie fully engaged. the wheel 53 abutting against the pivot pins of the pawls |00. Thereupon .the spring |26 operates to raise the abutment member |08 into place behind the thrust ring |05,

so as to prevent disengagement of the jaw-clutch teeth 06 and 90 when driving torque is re-applied and so lock the gearing in high gear.

In order to change from 11i-gh to low gear the control shaft ||3 is urged in the clockwise direction and the input torque is momentarily interrupted, for example by actuating a control mem- -ber of the engine. As the torque and with it the axial thrust on the wheel 93 fall. the abutment member |00 Is freed and withdrawn to its inoperative position while the abutment member |01 is pressed upwards. As the engine accelerates. the wheel 93 slides to the right under the reaction of its helical teeth, assisted by the reaction of the helical clutch teeth 53 and 90, taking with it the wheel 32 until the teeth 05 disengage from A first-speed driving wheel PI having twentyone helical teeth with a 30-deg. left-handed helix angle is fixed to the primary shaft |30 and is in constant mesh with a forty-seven tooth wheel SI, which accordingly has right-handed helical teeth. The wheel S| is slidable'and rotatable on the secondary shaft I 34. The wheel PI is integral with a tubular extension |44 provided with internal clutch teeth |45 having a left-handed helix angle of 15 degrees. The hub of the wheel Si has a kange |43 provided with left-handed 15-deg. helical clutch teeth |41, and pawls |40 having left-handed 15deg. helical noses are pivotally mounted on the rear of this ange. (The righthand end of the gear case, as viewed in Fig. 16, will be regarded as the front" and the left-hand end as the rear.) The noses of these pawls point in the direction of rotation indicated by the arrow.

A second-speed driving wheel P2 having thirty right-handed 30-deg. helical teeth is rigid with a sleeve |43 slidable and rotatable on the shaft |30 and is in constant mesh with a wheel S2 which has thirty-eight left-handed helical teeth and is nxed to the shaft |34. The sleeve |43 has a flange |50 provided with left-handed 15-deg. helical Jaw-clutch teeth I5| adapted to mesh cleanly with the teeth |45 under the control of pawls |52 and |53 which have corresponding helical noses. The pawls |52 on the front of the flange have their noses pointing in the normal direction of rotation, while the noses of the pawls |53 on the rear of this flange trail with respect to this direction of rotation. A one-way thrust bearing |54 has an inner race clamped. to the sleeve |43 by a nut |55 and an outer race mounted in an abutment ring |55 having an inwardly directed flange |51 located by the nut |55. Uniformly pitched axially projecting teeth |50 on the rear of the.. abutment ring |50 co-operate with axially projecting teeth |59 formed on the fixed housing of the bearing |32.

The wheel S2 has a forwardly projecting tubular extension |30 having internal left-handed 15deg. helical clutch teeth |3| adapted to mesh cleanly with theteeth |41 under control of the pawls |40.

A third-speed driving wheel P3 having thirtyeight right-handed 30deg. helical teeth isv rigid with a sleeve |62 slidable and rotatable on the shaft |30 and is in constant mesh with a wheel S3 which has thirty left-handed helical teeth and is fixed to the shaft |34. The sleeve |62 has a flange |63 provided with left-handed l5- deg. helical jaw-clutch teeth |64 adapted to mesh cleanly, under the control of pawls |65 and |66. which have -corresponding helical noses, with left-handed Iii-deg. helical jaw-clutch teeth |61 within a. tubular extension |68 of a sleeve |69 rigid with the shaft |30. The pawls |66 on the front of the flange |63 have their noses pointing in the normal direction f rotation, while the noses of the pawls |35 on the rear of this flange trail with respect to this direction of rotation. A one-way thrust bearing has an inner race clamped to the sleeve |62 by a nut |1| and an outer race mounted in an abutment ring |12,A

having an inwardly directed flange |13 located by the nut |1|. Uniformly pitched axially projecting teeth |14 on the rear of .the abutment ring |12 co-operate with axially projecting teeth |15 formed on the fixed housing of the bearing |33.

A fourth-speed driving wheel P4 having fortyseven teeth, which may be SO-deg. right-handed helical, is in constant mesh with a twenty-onev tooth wheel S4 fixed to the shaft |34, is journalled on the sleeve |69 and is rigid with the driven body |16 of a friction clutch having a driving plate |18 which can be clamped against a facing |19 on the body by a presser plate |11. The driving plate |18 is fixed to a hub |80 which is-splined to the shaft |30. This friction clutch is normally held in the disengaged condition shown by means of tension springs such as |8| connected between the front of the plate |11 and a cover |82 fixed to the body |16. Means for engaging the clutch include a slidable striking ring |83 having axial fingers such as |84 which project through apertures in the cover |82 and engage the inner ends of radial levers such as |85 the outer ends of which are pivotally connected to studs |86 secured to the cover |82 and which are adapted to bear, through the intermediary of balls |81 partly sunk in pockets |88 in the levers, on the presser plate |11. This clutch also includes oblique rockable struts |89 fitted between the presser plate |11 and the cover |82 and capable of assisting the engaging force in response to the application of driving torque, in the manner described 'in U. K. patent specification No. 508,088.

The gear wheel S3 is in constant mesh with a forward driving wheel |90 journalled on the shaft |31 and the gear wheel S4 is in constant mesh with a reverse idler wheel |9| (Fig. 17) journalled on a fixed pin |92 and meshing with a reverse driving wheel |93 also journalled on the shaft |31. The wheels |90 and |93 can be alternatively clutched to the shaft |31 by a jawclutch element |94 slidably splined to a collar |95 rigid with the shaft |31. This reversing jaw clutch element is actuated by any suitable shifting mechanism notvshown.-

A ganging bar |96 is so mounted in the' gear case |3| as to be slidable parallel to the gear shafts. A striking fork |91 fixed to the bar |96 nts closely in a groove |93 in the abutment ring |58, and a striking fork |90 also xed to the bar |06 isdisposed behind and adapted to co-opcrate with a flange 200 on the abutment ring |12. An arm fixed to the bar |9615 disposed with its end in front ot the iange |46 of the hub of the wheel SI.

The control mechanism is shown in the developed view in Fig. 18 and in Fig. 19. A gear-selectng controshaft 202 is journalled in the gear case |3| and to it are fixed levers 203 and 204 (Fig. 18) which are connected respectively by links 205 arid 206 to lugs 201 and 208 on the rings |56 and |12, whereby thcse rings can be displaced about the axis of the shaft |30. A gear-selecting control lever 209 (Fig. 19) operates in a fixed quadrant 2|0 and is rigid with an arm 2|| which is connected by a link 2|2 with a lever 2|3 fixed to the gear-selecting control shaft 202. The control lever is provided with a latch 2|4 adapted to lock it in each of the four positions denoted by 2, 3. and 4 and representing respectively first, second, third and fourth speeds. The positions ofthe levers 203 and 204 are similarly denoted in Fig. 18. These parts are shown in the first-speed position. The teeth |14 on the abutment ring |12 are narrower than-the gaps between the fixed teeth |15 with which they cooperate, with the result that the teeth |14 are in register with these gaps when the control mechanism is in second-'speed position also, under which condition the abutment ring |56 will have shifted to the front, in a manner to be described hereinafter, and the ends of the teeth |58 on that ring will overlap the ends of the teeth |59. When the control mechanism is in third-speed and fourth-speed positions, both abutment rings |56 and |12 will have been shifted to the front, and

the ends of the teeth |58 and |14 will respectivev ly overlap the ends of the teeth |59 and |15.

The striking ring |83 of the friction clutch is connected through a thrust bearing 2|5 (Fig. 16) to a non-rotatable ring 2|6 which is connected by opposed radialv pins such as 2|1 (Fig. 19) to a yoke 2|8 fast on a transverse shaft 2|9 carried by brackets such as 220. A lever 22| fixed to the shaft 2|9 is connected by a link 222 to the piston rod 223 of a pneumatic servo-motor 224 the cylinder of which is xed to the gear ease |3|, the arrangement being such that, when compressed air is supplied to the motor through a pipe 225, the piston is thereby forced rearwards, engaging the friction clutch. The pipe 225 connects to a piston valve body 226 to which are also connected a pipe 221 connecting with a rotary valve body 232 and a pipe 228 connected to a compressed air reservoir (not shown). piston 229 of this valve is connected by a link 230 with the gear control lever 209, the arrangement being such that, when the lever 209 is in first, second and third-speed positions, the pipes 225 and 221 communicate with each other' and the pipe 228 is sealed, and when the lever 209 is in the fourth-speed position, the pipes 225 and 228 communicate with each other and the pipe 221 is sealed.

The pipe 221 and a branch 23| from the supply pipe connect with the valve body 232 having a port 233 open to atmosphere. 'I'he body 232'contains an oscillatory plug 234 rigid with a lever 235 controlling the power output of the .engine 35A, which is of the compression-ignition type and includes a battery 236 of fuel-injection pumps the delivery of which is variable by actuation of a lever 231 shown in the idling position. The lever 235 is connected to the lever 231 -by a spring link 238 which is normally kept expanded as shown by a compression spring 239. The control lever 235 is movable between a position F, corresponding to full power. through the idling position shown, to a position S such that the lever 231, which cannot pass beyond the idling position, causes the spring link 238 to contract. When. the lever 235 is in the idling and Thel the full-power positions and anywhere between these positions. the rotary valve maintains the pipe 221 in communication with the port 233.and seals the pipe 23|. When the lever 235 is moved to position S, the rotary valve puts the pipes 221 and 23| into communication with each other and isolates the port 233.

.This mechanism operates asfollows. It will be assumed that the control levers are in the positions shown in Fig. 19, that the engine is idling, that thereverslng jaw-clutch element |34 is engaged with say the wheel |33, and that the locomotive is stationary. The hydraulic coupling urges the shaft |30 and the wheel PI to rotate. Since the wheel SI is prevented by the arm 20|, in a manner which will be hereinafter explained. from moving in front of the position in which it appears in Fig. 16, this wheel is prevented from rotating by engagement of a pawl |43 with a tooth |6|. The reaction of the helical teeth of the wheels P| and SI, assisted by the reaction of the pawl |40 and the helical :law-clutch tooth with which it is engaged, causes the wheel SI to slide rearwards so that the teeth |41 mesh cleanly with the teeth |3|. The lever 235 (Fig. 19) is now displaced towards position F, the engine accelerates, and the locomotive starts, the power being transmitted through shaft |30, wheels P| and Sl, jaw clutch |41, |6I, wheel S2, shaft |34, wheels S3 and |30, clutch member |34 and shaft |31. When the gear isv running thus in first speed, the shaft |33 rotates faster than the whee1P2; friction between this wheel and the shaft 30 thus causes a reaction between the meshing teeth of the wheels P2 and S2 which maintains the wheel P2 in its rearmost position,

such that the pawls 52 are behind the teeth |45 and therefore do not click over them. Likewise the shaft |30 rotates faster than the wheel P3 so that the reaction of the meshing helical teeth of the wheels P3 and S3 carrying the load due to friction between the wheel P3 and the shaft |30 maintains the wheel P3 in the position shown in Fig. 16, such that pawls do not click over the teeth |61. Since the. gauging bar |36 is constrained to shift with the wheel P2, it will assume its rearmost position. 4

In order to change to second speed, the engine control lever 235 is moved to-position S with the result that the engine fuel supply is reduced and the servo-motor 224 is energized engaging the friction clutch which while slipping serves to retard the shaft |30 by coupling it to the slowerrotating wheel P4 and also maintains the 'output of driving torque by expending the kinetic energy of the rotating elements in front of the gear box. At the same time the gear-selecting lever 203 is unlatched and urged towards position 2. As soon as the speed of the shaft |30 begins to fall relatively to that of the shaft |34, the torque reaction between the helical teeth of the wheels P| and SI, assisted by the reaction between the helical jaw-clutch teeth |41 and |3|, causes the wheel SI to slide to the front, disengaging these clutch teeth. Such sliding of the wheel Sl causes the flange |46 to slide the gauging bar |36 to lthe front through the agency of the arm so that the wheel P2 is slid to the front by the fork |31 until the pawls |52 come intothe path of and ratchet over the jaw-clutch teeth |45.

, When-the speed of the shaft begins to drop below that of the wheel P2, a pawl |52 engages a tooth |45, and the reaction between the helical teeth of the wheels P2 and S2, assisted by the reaction between the engaged pawl |52 and assent? helical tooth |45, causes the wheel P2 to slide to the front, the `iawutch teeth and |5| meshing cleanly toge er underthe control of the pawl |52. sliding of the when P2 continues P2 has slid so far to the front that the teeth |53 on the abutment ring |56 come out of mesh with the fixed teeth |53, the gear-selecting mechanism becomes free to move, and the driver latches the lever 203 in position 2 and returns the engine control lever 235 towards position F. In consequence the servo-motor 224 is le-energized, the friction clutch disengages, and the engine accelerates. When the shaft |33 tends to rotate faster than the wheel P2, a pawl |53 engages with a tooth |45, and the reaction thus introduced between the helical teeth of the wheels P2 and S2. assisted by the reaction between the pawl |53 and the tooth |45 with which it is engaged, causes the wheel P2 to slide to the rear, the jaw-clutch teeth 5| meshing cleanly with the teeth|45.

under control .of the pawl |53. As these teeth become fully engaged together, the ends of the teeth |53 on the abutment ring |53 abut the ends of the fixed teeth |53 so that the wheel P2 is prevented from sliding farther to the rear. Power is now transmitted from the shaft |33, through the parts PI and |44, the jaw-clutch |45, |5I, the wheels P2 and S2 and thence as on first speed. When second-speed driving conditions are established the wheels SI and .P3 slide, under the innuence of the helical tooth reactions due to frictional drag, respectively to their .foremost and rearxnost positions, so that no pawls will click idly over jaw-clutch teeth.

In order to change from second to third speed, the engine control lever is moved to position S. The resulting slipping engagement of the friction clutch retards the shaft |30 by coupling it to the wheel P4 which still rotates slower than the shaft |30, and also maintains the output of driving torque. At the same time the gear-selecting lever 203 is unlatched and moved towards position 3. As soon as the speed of the shaft |30 begins to fall relatively to that of the shaft |34, the torque reaction between thehelicai teeth of the wheels P2 and S2, assisted by the reaction between the helical jaw-clutch teeth |45 and |5|, causes the wheel P2 to slide to the front. disengaging these clutch teeth. Such sliding of the wheel P2 causes the ganging bar |33 to slide to the front, through the agency of the fork |31, so that the fork |33, abutting against the flange 200 on the abutment ring |12, causes the wheel P3 also to slide to the front until its pawls |66 come into the path of and ratchet over the jawclutch teeth |61. When the speed of the shaft |30 begins to drop below that of the wheel P3, a pawl |66 engages a tooth |61, and the-reaction between the helical teeth of the wheels P3 and S3. as-

sisted by the reaction between the engaged pawl |66 and helical tooth |61, causes the wheel P3 to slide to the front, the jaw-clutch teeth |34 and |61 meshing cleanly together under the control of the pawlIGG. Sliding' ofthe Wheel P3 continues until the pawls |65 come into the path of and ratchet over the teeth |61. As soon as the wheel P3 has slid so far to the front that the teeth |14 on the abutment ring |12 come out of mesh with the fixed teeth |15, the gear-selecting mechanism becomes free to move, and the driver'- latches the lever 209 in position 3 and returns the engine control lever towards position F, so that the servo-motor 224 is de-energized, the friction clutch disengages and the engine accelerates. When the shaft |30 tends to rotate faster than the -wheel P3, a pawl |65 engages with a tooth |61 and causes the wheel P3 to slide to the rear, the jaw-clutch teeth |64 meshing cleanly with the teeth |61 under control of the pawl |65. As these teeth become fully engaged together, the ends of the teeth |14 on the abutment ring |12 abut the ends of the fixed teeth |15 so that the wheel P3 is prevented from sliding farther to the rear. Power is now transmitted from the shaft |30, through the parts |69 and |66, the jaw clutch |61, |64. the wheels P3 and S3, and thence as before. When third-speed driving conditions are established. the wheel P2 slides, under the influence of the helical tooth reactions due to frictional drag, to its foremost position, so that its pawls |53 are in front of the clutch teeth |45 and therefore do not click idly.

Fourth speed is intended for use only when the locomotive is required'to run fast under a light load. and it is engagedby shifting the gear selecting lever 209 to position 4. Such movement displaces the valve piston 229 into a position such that the pipe 221 is isolated and compressed air is delivered directly from the pipe 226 to the pipe 225. The servo motor 224 is consequently kept energized, irrespective of the position of the en 5 gine control lever 235, and power is transmitted from the shaft |30, through the clutch parts |80 and |18, the clutch body |16, the wheels P4 and S4 and thence asbefore. Under these conditions the wheel P3 will be rotated faster than the shaft |30, and the reaction of its helical teeth meshing with those of the wheel S3` assisted by the reaction of the helical jaw-clutch teeth |64 and |61 will cause the wheel P3 to slide to its foremost position, in which the pawls |65 ratchet idly over the teeth |61.

The change from fourth to third speed is effected by shifting the gear-selecting lever 209 to position 3 While, if desired, maintaining the power output of theengine. Since the pawls |65 are in the path of the teeth |61, third speed will be established by sliding of the wheel P3 to the rear, so as to mesh the teeth |64 and |61 together, under the influence of the reaction of the helical teeth as the speed of the shaft |30 tends to exceed that of the wheel P3.

In changing from third to second speed, the gear-selecting lever 209 is unlatched and urged towards position 2; the engine control lever 235 is momentarily returned to the idling position in order to reduce the driving torque and thus relieve the abutment ring |12 of axial thrust. As soon as this thrust is reduced enough, the abutment ring |12 can rotate so as to its teeth |14 into register with the gaps between the fixed teeth |15 as the driver shifts the lever 266 into position 2. When the engine accelerates again, the reaction between the helical teeth of the wheels P3 and S3, assisted by the reaction between the helical jaw-clutch |64 and |61, slides the wheel P3 to the rear. The flange 266 on the ring |12 shifts the gauging bar |96 to the rear through the agency of the fork |93, so that the fork |61 carries the wheel P2 to the rear until the pawls |53 come into the path of and ratchet over the slower running teeth |45. When the speed of me shaft lal-teds to exceed that ofthe wnee1 P2, a pawl |53 engages with a -helical tooth |45 and the reaction thus generated between the helical teeth of the wheels P2 and S2, assisted'by the reaction between the engaged pawl |53 and tooth |45, causes the wheel P2 to slide to the rear, establishing second speed in the manner hereinbefore described.

The change from second to rst speed is initiated by unlatching the gear-selecting lever 209 and urging it towards position The engine control lever 235 is momentarily returned to the idling position, so as to reduce the driving torque and relieve the abutment ring |56 of axialthrust. As soon as this thrust is reduced enough, the ring |56 can rotate so as to bring its teeth |56 into register with the gaps between the xed teeth |59 as the driver shifts the lever 209 to position When the engine accelerates again, the reaction between the helical teeth of the wheels P2 and S2, assisted by the reaction between'the 'helical jaw-clutch teeth |45 and |5|, slides the wheel P2 to the rear. Such sliding of the wheel P2 causes the gauging bar |96 also to move to the rear so that the arm 20| slides the wheel S| to the rear until the pawls |48 come into the path of and ratchet over the faster running teeth |6|. When the speed of the wheel SI tends to exceed that of the shaft |34 and wheel S2, a pawl |46 engages with a tooth |6|, and the reaction thus generated between the helical teeth of the wheels PI and SI, assisted by the reaction between the engaged pawl |48 and tooth v|6|. causes the wheel SI to slide to the rear, establishing first speed through engagement of the jaw-clutch teeth |41 and |6|. y

It will thus be apparent that this gear, as is convenient on an oil-engine-driven locomotive, can free-wheel on all speeds except the highest.

The synchronizing coupling shown in Fig. 21 permits the shaft 24| to rotate in the direction indicated by the arrow relatively to the shaft 242, while the latter shaft can never rotate in the said direction relatively to the shaft 24|. A drum 243 rigid with the shaft 24| has internal lefthanded helical jaw-clutch teeth 244. An internally splined n'ng 245 is slidable on splines on the shaft 242 between stops 246 and 241 and is provided with external helical jaw-clutch teeth 240 adapted to mesh with the teeth 244 under the control of one or more pawls, such as 249. The noses 250 of those pawls are bevelled to the helix angle of the jaw-clutch teeth and so positioned as to engage a tooth 244, when the parts are in the conguration shown and the shaft 242 tends to rotate in the direction indicated by the arrow relatively to the shaft 24|, and so generate a reaction causing the ring 245 to slid'e to the left and cleanly engage the teeth 244 and 246 together. In order that the coupling can be locked so as to be capable of transmitting torque bi-directionally, the ring 245 may be provided with radially slidable bolts, such as 25|, urged outwards by springs 252. When the teeth 244 and 243 are engaged together, the inner ends of these bolts register with holes. such as 253, in the shaft 242 and can be .engaged with those holes, to lock the ring 245 to the shaft 242. The bolts are actuated by a striking sleeve 254 having tapered longitudinal grooves 256 adapted to accommodate lthe roundedA 0116er endsl of the bolts 25| and 60 move these bolts radially inwards when We claim:

1. In a toothed wheel power transmission gearing, a positive synchronizing coupling mechanism serving as a clutch for establishing a drive through said gearing and including a rst member, a second member rotatable relatively to said first member, an intermediate member in driving connection with said second member and capable of sliding relatively to said first and second members into and out of meshing engagement with said first member, and a subsidiary ratchet drive between said rst and intermediate members operative while these members are disengaged to synchronize them for meshing cleanly together when said first and second members are urged to rotate relatively to each other in one sense, wherein helical teeth are disposed on the exterior of said intermediate member to co-operate with helical teeth on one of the others of said members and thereby to effect sliding of-said intermediate member under the influence of torque transmitted through the mechanism.

2. In a toothed wheel power transmission gear- 'ng, a positive synchronizing coupling mechanism serving as a clutch for establishing a drive through said gearing and including a iirst member.having a set of clutch teeth, a second member in the'form of a helical toothed gear wheel disposed with its axis parallel to that of said first member, an intermediate member which is co-axial with said first member and which includes a set of clutch teeth and a helical toothed gear wheel meshing with said first-mentioned gear wheel, said intermediate member being slidable relatively to said first and second members, and a pawl mounted on one of said first and intermediate members and adapted to co-operate with the said set of clutch teeth on the other of said first and intermediate members when said sets of clutch teeth are disengaged, said pawl being operative to transmit torque in such a sense between said first member and said intermediate member that said helical gear wheels co-operate to cause said intermediate member to slide in the axial direction such that said sets of clutch teeth interengage cleanly under the registering action of said pawl.

3. In a toothed wheel power transmission gearing, a positive synchronizing coupling mechanism serving as a clutch for establishing a drive through said gearing and including a first member having a set of helically disposed clutch teeth, a second member co-axial with and rotatable relatively to said rst member, an intermediate member co-axial with and slidable relatively to said first and second members and drivably connected to said second member, said intermediate member including a set of helically disposed clutch teeth adapted to co-operate with said clutch teeth on said rst member, and a pawl onvone of said rst and intermediate members so positioned that, when said sets of clutch teeth are disengaged from each other and said mechanism is under torque load in one sense, said pawl co-operates with one of said helical clutch teeth on the other of said first and intermediate members and thereby causes a reaction urging said intermediate member axially in such a direction as to engage said sets of clutch teeth cleanly together.

4. In a toothed wheel power transmission gearing, a positive synchronizing coupling mechanism serving as a clutch for establishing a drive through said gearing and including a first member having a set of clutch teeth, a second memmember, an intermediate member which is coaxial with said first member and which includes a set of clutch teeth and a helical toothed gear Wheel meshing with said first-mentioned gear wheel, said intermediate member being slidable relatively to said first and second members, and a pawl mounted cn one of said first and intermediate members and adapted to co-operate with the said set of clutch teeth on the other of said first and intermediate members when said sets of clutch teeth are disengaged, said pawl being operative to transmit torque in such a sense between said first member and said intermediate member that said helical gear wheels co-operate to cause said intermediate member to slide in the axial direction such that said sets of clutch teeth interengage cleanly under the registering action of said pawl, said two sets of clutch teeth being helically disposed in such a sense that, when the mechanism is under torque load acting in one sense, the torque reaction due to said pawl and one of said helical clutch teeth with which it co-operates in one condition, and the torque reaction due to the inter-engaged helical'fciutch'fteeth,in another condition, both urge the intermediate member in the same axial direction as does the torque reaction due to the co-operating helical gear wheels.

5. In a toothed Wheel power transmission gearing, a positive synchronizing coupling mechanism serving as a clutch for establishing a drive through said gearing and including a first member, a second member rotatable relatively to said first member, an intermediate member in driving connection with said second member and capable of sliding relatively to said first and second members into and out of meshing engagement with said first member, and a subsidiary ratchet drive between said first and intermediate members operative while these members are disengaged to synchronize them for meshing cleanly together when said first and second members are urged to rotate relatively to each other in one sense, helical teeth disposed on the exterior of said intermediate member to co-operate with helical teeth on one of the others of said members and thereby to effect sliding of said intermediate member under the influence of torque transmitted through the mechanism, and means operable for preventing sliding movement of said intermediate member such as to cause'disengagement from each other, in at least one relative direction, of said sets of clutch teeth, said means including a thrust bearing associated with said intermediate member and an abutment member displaceable by control means and adapted to co-operate with said thrust bearing.

6. In a toothed wheel power transmission gearing, a, mechanism as claimed in claim 5, wherein said abutment member is provided with a wedging surface so disposed as to initiate engaging movement of said intermediate member.

7. In a toothed wheel power transmission gearing, a positive synchronizing coupling mechanism serving'as a clutch for establishing a drive wheel, said intermediate member being slidable relatively to said iirst and second members, a pawl mounted on one of said ilrst and intermediate members and adapted to co-operate with the said set of clutch teeth on the other of said first and intermediate members when said sets of clutch teeth are disengaged, said pawl being operative to transmit torque in such a sense between said rst member and said intermediate member that said helical gear wheels co-operate to cause said intermediate member to slide in the axial direction such that said sets of clutch teeth interengage cleanly under the registering action of said pawl, and means operable for preventing sliding movement of said intermediate member such as tb cause disengagement from each other, in at least one relative direction. of said sets of clutch teeth, said means including a thrust bearing associated with said intermediate member and an abutment member displaceable by control means and adapted to `co-operate with said thrust bearing.

8. In a toothed wheel power transmission gearing. a positive synchronizing coupling mechanism serving as a clutch for establishing a drive through said gearing and including a nrst member having a set oi clutch teeth. a second member in the form of a helical toothed gear wheel disposed with its axis parallel to that of said first membenan intermediate member which is co-axial with said iirst member and which includes a set of clutch teeth and a helical toothed gear wheel meshing with said mst-mentioned gear wheel, said intermediate member being slidable relatively to said nrst and second members, a pawl mounted on one of said ilrst and intermediate members and adapted to co-operate with the said set of clutch teeth on the other of said rst and intermediate members when said sets of clutch teeth are disengaged, said pawl being operative to transmit torque in such a sense between said rst member and said intermediate member thatY said helical gear wheels co-operate to cause said intermediate member to slide in the axial direction such that said sets of clutch teeth interengage cleanly under the registering action of said pawi, a thrust bearing associated with said intermediate member, and an abutment member co-operating with said thrust bearing and movable at least in part radially with respect to the axis of said ilrst and intermediate members, said abutment member being capable f said thrust bearing includes a non-rotatable member co-operating with said abutment member and carrying a Michell thrust pad co-operating with said intermediate member.

10. In a toothed wheel power transmission gearing, a mechanism as claimed in claim 7, wherein said abutment member is provided with a wedging surface capable, when said sets of clutch teeth are disengaged, ot sliding said intermediate member irom a position such that said pawl is inoperative to a position such that it is operative.

1l. In a toothed wheel power transmission gearing, a mechanism as claimed in claim 5, and including a iirst abutment member associated with said thrust bearing, and a second abutment member incapable of axial displacement, said abutment members having interengageable teeth, and said control means being operable for causing relative angular displacement ot said abutment members to bring their teeth into and out of meshing Peli-Ster.

12. In a toothed wheel power transmission gearing, a mechanism as claimed in claim 5, wherein said abutment member is capable of angular displacement under the influence of said control means about the axis o! said iirst and intermediate members and is provided with teeth co-operating with teeth on a nxed part, the arrangement being such that, when said abutment member is in one angular position, said teeth can intermesh and, when said abutment member is in another angular position, said teeth are adapted to abut together out of meshing register.

13. In a toothed wheel powerv transmission gearing, a positive synchronizing coupling mechanism serving as a clutch for establishing a drive through said gearing and including a rst member having a set of clutch teeth, a second member in the form o! a helical toothed gear wheel disposed with its axis parallel to that oi said first member, an intermediate member which is coaxial with said mst member and which includes a set of clutch teeth and a helical toothed gear wheel meshing with'said first-mentioned gear wheel, said intermediate member being slidable relatively to said rst and second members, a pawl mounted on one of said iirst and intermediate members and adapted to co-operate with the said set of clutch teeth on the other of said rst and intermediate members when said sets of clutch teeth are disengsed. said pawl being operative to transmit torque in such a sense between said rst member and said intermediate lmember that said helical gear wheels co-operate to cause said intermediate member to slide in the axial direction such that said sets oi. clutch teeth interengage cleanly under the registering action of said pawl, a thrust bearing associated with said intermediate member, a toothed abutment member co-operating with said thrust bearing, a second abutment member incapable oi axial displacement and having teeth capable of intermeshing with the teeth of said ilrst abutment member, and control means for causing relative angular displacement of said abutment members between a position such that their teeth can. intermesh and a position such that their teeth are adapted to abut together out of meshing register and thereby prevent disengagement, in at least one relative direction, of said sets oi jaw-clutch teeth.

14. In a toothed wheel power transmission gearing, a mechanism as claimed in claim 7, wherein said abutment member is capable o f angular displacement under the influence of said control means about the axis of said tlrst and intermediate members and is provided with teeth co-operating with teeth on a ilxed'part, the arrangement being such that, when said abutment member is in one angular position, said teeth can intermesh and, when said abutment member is in another angular position, said teeth are adapted to abut together out of meshing register.

15. In multi-ratio change-speed gearing, two positive synchronizing coupling mechanisms serving as gear-selecting clutches and each in'- cluding a nrst member, a second member rotatable relatively to said ilrst member, an intermediate member in driving connection with said second member and capable of sliding relatively to said rst and second members into and out of meshing engagement with said rst member, a subsidiary ratchet drive between said ilrst and intermediate members operative while these members are disengaged to synchronize them for meshing cleanly together when said first and second members are urged to rotate relatively to each other in one sense, and helical torque'- transmitting surfaces on said intermediate member to co-operate with helical torque-transmitting surfaces on one of the others of said members and thereby to effect sliding of said intermediate member under the influence of -torque transmitted through the mechanism, the intermediate members of said two mechanisms being connected together by a ganging connection so arranged that sliding of one of said intermediate members in at least one direction imparts a sliding movement to the other of said intermediate members.

16. In multi-ratio change-speed gearing, two positive synchronizing coupling mechanisms serving as gear-selecting clutches and each including a iirst member having a set of clutch teeth, a second member. rotatable relatively to said rst member, an intermediate member drivably connected to said second member by means constraining said intermediate member to slide relatively to said first and second members on reversal of torque through said means, said intermediate member having a set of clutch teeth engageable with said clutch teeth of said rst member and being slidable in both axial directions from its position in which said sets of clutch teeth are intermeshed, a pawl on one of said two members which have the clutch teeth, said pawl being engageable with teeth on the other of said two members to effect meshing of said sets of clutch teeth together in one direction, an additional pawl on one of said two members engageable with teeth on the other of said two members to effect meshing of said sets of clutch teeth together inthe other direction, and control means operable to prevent sliding movement of said intermediate member in at least one axial direction from its said position, the intermediate members of these two positive synchronizing coupling mechanisms being connected together by a ganging connection which provides lost motion such that, when the two sets of clutch teeth of one of said mechanisms are engaged together, the two sets of clutch teeth of the other of said mechanisms can be disengaged and the pawls of said other of the mechanisms can be inoperative, and that disengagement 'of the sets of clutch teeth of said one of the mechanisms slides the intermediate member of said other of the mechanisms to a position such that one of the pawls of said other of the mechanisms becomes operative.

17, In multi-ratio change-speed gearing, two positive synchronizing coupling mechanisms `serving `as gear-selecting clutches and each including a rst member having a set of clutch teeth, a second member rotatable relatively to said Afirst member, an intermediate member drivably connected -to said second member by means constraining said intermediate member to slide members to eiect meshing of said sets oi clutch teeth together in one direction, at least one of said positive synchronizing coupling mechanisms also having an additional pawl on one o1' said two members which have the clutch teeth, said additional pawl being engageable with teeth on the other of said two members to effect meshlng of said sets of clutch teeth together in the other direction and control means operable to prevent sliding movement of the intermediate member of said one of the coupling mechanisms, the intermediate members of these two positive synchronizing coupling mechanisms being connected together by a ganging connection which provides lost motion such that, when the two sets of clutch teeth o! the other oi said mechanisms are engaged together, the two sets of clutch teeth of said one of the mechanisms can be disengaged and the pawls of said one of the mechanisms can be inoperative, and that disengagement of the sets of clutch teeth of said other ofthe mechanisms slides the intermediate member of said one oi' the mechanisms to a podtion such that one of the pawls oi said one oi' the mechanisms becomes operative.

18. Mechanism as claimed in claim 16, wherein each of said positive synchronizing coupling mechanisms includes a thrust bearing associated with said intermediate member, a toothed abutment member co-operating with said thrust bearing, a second abutment member incapable of axial displacement and having teeth capable of intermeshing with the teeth of said first abutment member, and control means for causing relative angular displacement-of said abutment members between a position such that their teeth can intermesh and a position such that their teeth are adapted to abut together out of meshing registerI and thereby prevent disengagement, in at least one relative'direction, oi' said sets oi' Jaw-clutch teeth, the control means oi' both of said coupling mechanisms being operatively connected tc a common control member, and the abutment members oi' at least one of said coupling mechanisms being capable, when their teeth are intermeshed, of relative angular displacement suiiicient to permit said control member to relatively dispiace the abutment members of the other of said coupling mechanisms between their intermeshing and their abutting relationships.

19. In a toothed wheel power transmission gearing, a positive synchronizing coupling mechanism serving as a clutch for establishing a drive through said gearing and including a lirst member having helical jaw-clutch teeth, a second relatively to said rst and second members on member rotatable relatively to said iirst member, an intermediate member in driving connection with said second member, said intermediate member having helical jaw-clutch teeth engageable, upon slidlng of said intermediate member relatively to said nrst member, with the Jawclutch teeth of said rst member, and a pawl mounted on one of said toothed members and having a nose bevelled to the helix angle o! said jaw-clutch teeth, said pawl being so positioned f as to be capable of engaging a tooth ot the other of said toothed members and thereby generating a reaction urging said intermediate member to mesh cleanly with said first member.

20. In a toothed wheel power transmission gearing, a positive synchronizing coupling mechanism serving as a clutch forestablishing a drive through said gearing and including a met member having a set of helically disposed clutch l teeth, ausecond member in the form of a helically toothed gear wheel, an intermediate member which is co-axial with said rst member and which includes a set of helically disposed clutch teeth and a helically toothed gear wheel meshing 5 with said mst-mentioned Sear wheel, said intermediate member being siidable relatively to said first and second members, and a pawl mounted on one o! said i'irst and intermediate members for co-operation with the Jaw-clutch teeth of the other of said rst and intermediate members when said sets of clutch teeth are disenassisted by the reaction of the pawi engaged with l0 a helical jaw-clutch tooth.

. HAROLD SINCLAIR.

ROBERT Cm CLERK. 

